CN105276143A - Transmission - Google Patents
Transmission Download PDFInfo
- Publication number
- CN105276143A CN105276143A CN201510410471.4A CN201510410471A CN105276143A CN 105276143 A CN105276143 A CN 105276143A CN 201510410471 A CN201510410471 A CN 201510410471A CN 105276143 A CN105276143 A CN 105276143A
- Authority
- CN
- China
- Prior art keywords
- switching member
- gear
- axle
- planet
- gear train
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H2003/442—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion comprising two or more sets of orbital gears arranged in a single plane
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2306/00—Shifting
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
A transmission (G) is provided having four planetary gear sets (P1, P2, P3, P4), several shafts (W1-W8) and a first, second, third, fourth and fifth shift element, the selective meshing of which brings about different transmission ratio relationships between a transmission input shaft (GW1) and a transmission output shaft (GW2). Two components of the second planetary gear set (P2) are connected through a fourth shift element (K2), the gear ring (Ho-P2), the planet carrier (St-P2), and a sun gear (So-P2) of the second planetary gear set (P2) have the same rotating speed when the fourth shift element (K2) is closed, and the second shaft (W2) is connected with the eighth shaft (W8) through a fifth shift element (K3).The transmission (G) includes a sixth shift element (K4), through which the fifth shaft (W5) is connectable to the sun gear (So-P4) of the fourth planetary gear set (P4).
Description
Technical field
The present invention relates to a kind of speed changer, comprise four planetary gear set, multiple axle and first, second, 3rd, 4th and the 5th switching member, the selectivity of switching member engages the different drive ratios caused between transmission input shaft and transmission output shaft, first axle is for good and all connected with the planet carrier of transmission input shaft and third planet gear train, second axle is for good and all connected with the planet carrier of transmission output shaft and first planet gear train, 3rd axle for good and all to connect with the sun gear of third planet gear train and can be fixed into and can not relatively rotate via the first switching member, 5th axle is for good and all connected with the gear ring of the second planetary gear set, 6th axle is for good and all connected with the gear ring of first planet gear train, the gear ring of third planet gear train is for good and all connected with the sun gear of the second planetary gear set and forms the constituent element of the 7th axle, 8th axle is for good and all connected with the planet carrier of the second planetary gear set, first axle can be connected with the sun gear of fourth planet gear train via the 3rd switching member, can be connected to each other by two elements of the 4th switching member second planetary gear set, make the gear ring of the second planetary gear set when the 4th switching member closes, planet carrier and sun gear have same rotational speed, and the second axle can be connected with the 8th axle via the 5th switching member.The invention still further relates to a kind of power assembly system for Motor Vehicle comprising this speed changer.
Background technique
This speed changer is mainly used in Motor Vehicle, so that in a suitable manner according to rotating speed and the torque output capability of the running resistance adjustment driver element of vehicle.
Disclose a kind of multiple-speed gear-box according to claim 1 preamble by the patent application DE102005014592A1 of the applicant, this multiple-speed gear-box comprises eight forward gears.
Summary of the invention
Task of the present invention is that by transmissions improved disclosed in prior art be the speed changer with nine forward gears.Another task of the present invention is the alternate embodiments providing speed changer disclosed in prior art.
This task is solved by the feature of claim 1, and favourable scheme is provided by dependent claims, specification and accompanying drawing.
According to the present invention, be additional to the element mentioned in independent claims 1 preamble and the 6th switching member is set, can be connected with the sun gear of fourth planet gear train by the 6th switching member the 5th axle.By the connection that can not relatively rotate before switchably taking apart between the gear ring and the sun gear of fourth planet gear train of the second planetary gear set, form an additional gear position, this gear comes between the 4th and fifth gear in the velocity ratio order of speed changer disclosed in prior art.This additional gear position be used as new fifth gear and by closed second, third, the 4th and the 5th switching member formed.First switching member and the 6th switching member are opened in new fifth gear.In other gears all, the 6th switching member closes.
Fourth gear and the speed ratio interval now between sixth gear is reduced by new fifth gear.Thus speed changer can in for Motor Vehicle time adapt to the consumption characteristic of internal-combustion engine better, internal-combustion engine is connected with transmission input shaft driving effect.Thus can the oil consumption of reduce engine motor-car.
Fourth planet gear train can be made to add in the power stream of speed changer by closed second switching member.This function realizes by multiple functionally identical embodiment, described embodiment will be described below.
According to the first embodiment, the 4th axle is fixed into can not relatively rotates by the second switching member.When fourth planet gear train is configured to negative ratio gear group, the gear ring of fourth planet gear train is the constituent element of the 4th axle and the 6th axle is for good and all connected with the planet carrier of fourth planet gear train.When fourth planet gear train is configured to positive drive than gear train, the planet carrier of fourth planet gear train is the constituent element of the 4th axle and the 6th axle is for good and all connected with the gear ring of fourth planet gear train.3rd axle is for good and all connected with the sun gear of first planet gear train in the first embodiment.
According to the second embodiment, the 6th axle can be connected via the planet carrier of the second switching member with the fourth planet gear train being configured to negative ratio gear group, and the gear ring of fourth planet gear train is the constituent element of the 4th axle and is fixed into and can not relatively rotates.Can not relatively be rotatably connected by gear ring, simplifies the structure of speed changer, because gear ring can be fixed into and can not relatively to rotate on case of transmission.Eliminate otherwise the radial and axial supporting device for sluing mechanisms of the gear ring needed.When fourth planet gear train is configured to positive drive than gear train, 6th axle can be connected via the gear ring of the second switching member with fourth planet gear train, and the planet carrier of fourth planet gear train is the constituent element of the 4th axle and is for good and all fixed into and can not relatively rotates.In the second embodiment, the 3rd axle is for good and all connected with the sun gear of first planet gear train.Compared with the first embodiment, the speed discrepancy appeared in the second embodiment on the second switching member is less, thus reduces the heat load of the second switching member.
According to the third embodiment, the 3rd axle can be connected via the sun gear of the second switching member with first planet gear train.4th axle is fixed into and can not relatively rotates.When fourth planet gear train is configured to negative ratio gear group, the gear ring of fourth planet gear train is the constituent element of the 4th axle and the 6th axle is for good and all connected with the planet carrier of fourth planet gear train.Embodiment is identical with the second, simplifies the structure of speed changer by can not being relatively rotatably connected of gear ring.When fourth planet gear train is configured to positive drive than gear train, the planet carrier of fourth planet gear train is the constituent element of the 4th axle and the 6th axle is for good and all connected with the gear ring of fourth planet gear train.In the third embodiment, treat that the support moment applied by the second switching member is less than first and second kinds of embodiments, because establish the connection with sun gear.Second switching member can construct less and lighter thus.
Speed changer has nine forward gears.First forward gear is formed by closed first switching member, the second switching member, the 3rd switching member and the 6th switching member.Second forward gear is formed by closed first switching member, the second switching member, the 4th switching member the 6th switching member.3rd forward gear is formed by closed second switching member, the 3rd switching member, the 4th switching member and the 6th switching member.4th forward gear is formed by closed second switching member, the 4th switching member, the 5th switching member and the 6th switching member.5th forward gear is formed by closed second switching member, the 3rd switching member, the 4th switching member and the 5th switching member.6th forward gear is formed by closed second switching member, the 3rd switching member, the 5th switching member and the 6th switching member.7th forward gear is formed by closed 3rd switching member, the 4th switching member, the 5th switching member and the 6th switching member.8th forward gear is formed by closed first switching member, the 3rd switching member, the 5th switching member and the 6th switching member.9th forward gear is formed by closed first switching member, the 4th switching member, the 5th switching member and the 6th switching member.Reverse gear by closed first switching member, the second switching member, the 5th switching member and the 6th switching member formation.
According to an embodiment of the present, speed changer has the 7th switching member.Can be connected with the 8th axle of speed changer by the 7th switching member first axle.Speed changer obtains another additional gear position and therefore has ten forward gears altogether thus.The high transmission ratio of feature in this case between transmission input shaft and transmission output shaft of described additional gear position.In other words, obtaining the extra high first gear of velocity ratio by adding the 7th switching member speed changer, which thereby enhancing the ratio coverage of speed changer.The first gear that this velocity ratio is high passes through to close first, second, the 6th and the 7th switching member realizes.In other gears all, the 7th switching member is opened.The formation of all the other nine forward gears and the transmission-like with nine forward gears described above are seemingly, thus the formation of the first of nine shift transmissions to the 9th forward gear is corresponding to the formation of the second to the tenth forward gear of ten shift transmissions, and the 7th switching member is opened in the second to the tenth forward gear.
Preferably the 7th switching member does not have infinitely variable torque transmission capacity.Such as the 7th switching member is configured to castellated switching member or synchronizer.Because the 7th switching member is except all opening, so reduce to pull to lose by this mode compared with the conventional friction formula switching member with variable torque transfer rate in external other nine forward gears all of first gear.
Replace negative ratio gear group, the fourth planet gear train of concrete speed changer can be configured to positive drive and compare gear train.In principle when the connection exchange with planet carrier and gear ring and the value of fixed drive ratio increases by 1 time, any negative ratio gear group can be replaced than gear train by positive drive.In concrete speed changer, particularly fourth planet gear train is applicable to being configured to positive drive than gear train, because this planetary gear set is mainly in the power stream of speed changer in low gear.In nine shift transmissions described above, the second switching member is only closed in the first to the 6th forward gear, and therefore fourth planet gear train is only in the power stream of speed changer in these gears.In ten shift transmissions described above, the second switching member is only closed in the first to the 7th forward gear.Therefore positive drive does not play a decisive role than more inefficient when gear train is in for vehicle transmission, because the efficiency of loss to Motor Vehicle in a motor vehicle in especially high gear has a negative impact.
6th switching member is except closed in the fifth gear of nine shift transmissions or the external all forward gears of the sixth gear of ten shift transmissions.Therefore, in each gear, four switching members of six or seven switching members close, and the efficiency of speed changer does not reduce based on the towing loss caused by least one additional switching member described thus.It is especially true when the 7th switching member is configured to castellated switching member.
Preferably the second switching member does not have infinitely variable torque transmission capacity.Such as the second switching member is configured to castellated switching member or synchronizer.Because the second switching member is only only opened from during the seven to the eight forward gear from during the six to the seven forward gear or ten shift transmissions described above, the moment of torsion produced when this switching member is thrown off is relatively little, and therefore the second switching member is particularly suitable for being configured to castellated switching member.Because the second switching member is especially opened to the 9th or the 8th to the tenth gear at high forward gear, namely the 7th, the design of castellated switching member can improve the efficiency of speed changer in high gear, because castellated switching member causes less towing loss in open mode compared with friction type switching member.It is particularly important when this is in for vehicle transmission.
Preferred third planet gear train is arranged on the radially inner side of the second planetary gear set.Significantly can reduce the axial arrangement space requirement of speed changer thus.This is especially significant in the vehicle transmission for lateral dynamics assembly system before having.
Speed changer can be the constituent elements of automotive drive train.Power assembly system also comprises internal-combustion engine except speed changer.Internal-combustion engine directly or by clutch or to be connected with transmission input shaft by fluid torque converter maybe can be connected.In order to reduce torsional oscillation, in the effect connection between internal-combustion engine and transmission input shaft, torshional vibration damper can be set.
" axle " not only comprise such as cylindrical rotatable supporting, for the machine element of transfer of torque, and general connecting element can be comprised, it connects each component or element, especially by connecting element that multiple element can not be rotatably connected each other relatively.
Planetary gear set comprises sun gear, planet carrier and gear ring.Planet carrier is rotatably supported with planetary pinion, and described planetary pinion engages with the teeth portion of sun gear and/or the teeth portion of gear ring.Negative ratio gear group represents and comprises planet carrier, sun gear and gear ring, planet carrier is rotatably supported with planetary pinion, at least one planetary teeth portion said is not only with the teeth portion of sun gear but also engage with the teeth portion of gear ring, thus, when sun gear rotates when planet carrier is fixing, gear ring and sun gear rotate round about.
Positive drive is than the difference of gear train with just now described negative ratio gear group, and positive drive comprises inner side and outer side planetary pinion than gear train, and described planetary pinion can be rotated to support on planet carrier.The teeth portion of inner planet geear engages with the teeth portion of outer planet gear with the teeth portion of sun gear on the one hand on the other hand at this.The teeth portion of outer planet gear engages with the teeth portion of gear ring in addition.This causes when planet carrier is fixed, and sun gear and gear ring rotate to equidirectional.
Fixed gear ratio is defined in the sun gear of planetary gear set and the rotating ratio of gear ring when planet carrier is fixed.Due to sun gear and gear ring counterrotating when planet carrier is fixed in negative ratio gear group, therefore fixed drive ratio is always negative value in negative ratio gear group.
Passing through switching member can realize the relative movement between two components or the connection of setting up between the two components for transfer of torque---according to its serviceability---." relative movement " such as can be regarded as the rotation of two components, the rotating speed of this first component and the rotating speed of second component different.Also can expect that only one of two components rotate in addition, and another member stationary or rotate round about.
When there is connection that is fixing, that especially can not relatively rotate between the two elements, two elements are especially called as " being connected to each other ".The element of connection like this rotates with same rotational speed.Different component of the present invention and element this can via axle or via closed switching member or connecting element but also can directly, such as by welding, compression is connected or other connection is connected to each other.
When there is separable can not being relatively rotatably connected between the two elements, two elements are called as " can/can connect ".When there is this connection, then described element rotates with same rotational speed.
Accompanying drawing explanation
Below with reference to the accompanying drawings embodiments of the invention are described in detail.Accompanying drawing is as follows:
Fig. 1 schematically shows the speed changer according to prior art;
Fig. 2 schematically shows the speed changer according to the first embodiment;
Fig. 3 illustrates the gearshift figure of the first embodiment of speed changer;
Fig. 4 schematically shows the speed changer according to the second embodiment;
Fig. 5 schematically shows the speed changer according to the third embodiment;
Fig. 6 schematically shows the speed changer according to the 4th kind of embodiment;
Fig. 7 schematically shows the speed changer according to the 5th kind of embodiment;
Fig. 8 schematically shows the speed changer according to the 6th kind of embodiment;
Fig. 9 schematically shows the speed changer according to the 7th kind of embodiment;
Figure 10 schematically shows the speed changer according to the 8th kind of embodiment;
Figure 11 schematically shows the speed changer according to the 9th kind of embodiment;
Figure 12 illustrates the gearshift figure according to speed changer the 9th kind of embodiment.
Embodiment
Fig. 1 schematically shows the speed changer according to prior art.This speed changer comprises four planetary gear set P1, P2, P3, P4, and they are all configured to negative ratio gear group.Third planet gear train P3 is arranged on the radially inner side of the second planetary gear set P2, and the gear ring Ho-P3 of third planet gear train is connected with the sun gear So-P2 of the second planetary gear set P2 and is the constituent element of the 7th axle W7.The sun gear So-P3 of third planet gear train P3 is the constituent element of the 3rd axle W3 and is connected with the sun gear So-P1 of first planet gear train P1.The planet carrier St-P3 of third planet gear train P3 is connected with transmission input shaft GW1 and is the constituent element of the first axle W1.The planet carrier St-P2 of the second planetary gear set P2 is the constituent element of the 8th axle W8.The gear ring Ho-P2 of the second planetary gear set P2 is the constituent element of the 5th axle W5 and is connected with the sun gear So-P4 of fourth planet gear train P4.The gear ring Ho-P4 of fourth planet gear train P4 is the constituent element of the 4th axle W4.The planet carrier St-P1 of first planet gear train P1 is the constituent element of the second axle W2 and is connected with transmission output shaft GW2.The gear ring Ho-P1 of first planet gear train P1 is the constituent element of the 6th axle W6 and is connected with the planet carrier St-P4 of fourth planet gear train P4.
Can not can not can be connected with the relative rotation by relative rotating member with another of case of transmission GG or speed changer by the first switching member B1 the 3rd axle W3.Be fixed in a similar manner can not relatively rotate by second switching member B2 the 4th axle W4.Can be connected with the sun gear So-P4 of fourth planet gear train P4 by the 3rd switching member K1 first axle W1.Can be connected with sun gear So-P2 by the gear ring Ho-P2 of the 4th switching member K2 second planetary gear set P2.When the 4th switching member K2 closes, sun gear So-P2, the planet carrier St-P2 of the second planetary gear set P2 and gear ring Ho-P2 rotate with same rotating speed.Can be connected with the second axle W2 by the 5th switching member K3 the 8th axle W8.
Fig. 2 schematically shows the speed changer G according to the first embodiment of the present invention.Be different from speed changer well known in the prior art, the 6th switching member K4 is arranged in the power stream between the gear ring Ho-P2 of the second planetary gear set P2 and the sun gear So-P4 of fourth planet gear train P4.
Fig. 3 schematically shows the gearshift figure according to the first embodiment of speed changer G.At this to go explanation nine forward gears 1 to 9 and the R that reverses gear.In phase assortment, represent which switching member B1, B2, K1, K2, K3, K4 must be closed, to realize corresponding gear 1-9, R by X.
First forward gear 1 is formed by closed first switching member B1, the second switching member B2, the 3rd switching member K1 and the 6th switching member K4.Second forward gear 2 is formed by closed first switching member B1, the second switching member B2, the 4th switching member K2 and the 6th switching member K4.3rd forward gear 3 is formed by closed second switching member B2, the 3rd switching member K1, the 4th switching member K2 and the 6th switching member K4.4th forward gear 4 is formed by closed second switching member B2, the 4th switching member K2, the 5th switching member K3 and the 6th switching member K4.5th forward gear 5 is formed by closed second switching member B2, the 3rd switching member K1, the 4th switching member K2 and the 5th switching member K3.6th forward gear 6 is formed by closed second switching member B2, the 3rd switching member K1, the 5th switching member K3 and the 6th switching member K4.7th forward gear 7 is formed by closed 3rd switching member K1, the 4th switching member K2, the 5th switching member K3 and the 6th switching member K4.8th forward gear 8 is formed by closed first switching member B1, the 3rd switching member K1, the 5th switching member K3 and the 6th switching member K4.9th forward gear is formed by closed first switching member B1, the 4th switching member K2, the 5th switching member K3 and the 6th switching member K4.The R that reverses gear is formed by closed first switching member B1, the second switching member B2, the 5th switching member K3 and the 6th switching member K4.
Fig. 4 schematically shows the speed changer G according to the second embodiment of the present invention.Different from the first embodiment, fourth planet gear train P4 is configured to positive drive and compares gear train in the second embodiment.Corresponding therewith, axle W6, the W4 be connected on gear ring Ho-P4 and planet carrier St-P4 exchanges.6th axle W6 is connected with the gear ring Ho-P4 of fourth planet gear train P4 now, and the 4th axle W4 connects with the planet carrier St-P4 of fourth planet gear train P4 now and can be fixed into and can not relatively rotate via the second switching member B2.When fourth planet gear train P4 is configured to positive drive than gear train, except the corresponding relation of gear ring and planet carrier exchanges, the value of fixed drive ratio improves 1, to realize the transmission effect identical with negative ratio gear group.
Fig. 5 schematically shows the speed changer G according to the third embodiment of the present invention.Different from the first embodiment, the 4th axle---it connects with the gear ring Ho-P4 of fourth planet gear train P4 in the present embodiment---is permanently fixed into and can not relatively rotates.In power stream between the planet carrier St-P4 that second switching member B2 is arranged on the 6th axle W6 and fourth planet gear train P4 in the present embodiment.
Fig. 6 schematically shows the speed changer G according to the present invention the 4th kind of embodiment.Different from the third embodiment, fourth planet gear train P4 is configured to positive drive and compares gear train.Corresponding therewith, in the power stream between the gear ring Ho-P4 that the second switching member B2 is arranged on the 6th axle W6 and fourth planet gear train P4 now, and the 4th axle W4 forever connects with planet carrier St-P4 and be fixed into and can not relatively rotate.The fixed drive ratio of fourth planet gear train is as adjustment corresponding in the second embodiment.
Fig. 7 schematically shows the speed changer G according to the present invention the 5th kind of embodiment.Identical with the third embodiment, the 4th axle W4 is permanently fixed in the present embodiment and can not relatively rotates.In power stream between the sun gear So-P1 that second switching member B2 is arranged on the 3rd axle W3 and first planet gear train P1 in the present embodiment.
Fig. 8 schematically shows the speed changer G according to the present invention the 6th kind of embodiment.Identical with the 5th kind of embodiment, in the power stream between the sun gear So-P1 that the second switching member B2 is arranged on the 3rd axle W3 and first planet gear train P1.But fourth planet gear train P4 is configured to positive drive than gear train, forever connects with the planet carrier St-P4 of fourth planet gear train P4 and be fixed into can not relatively rotate at this 4th axle W4.The gear ring Ho-P4 of fourth planet gear train P4 is connected with the 6th axle W6.
Fig. 9 schematically shows the speed changer G according to the present invention the 7th kind of embodiment.Different from first to the 6th kind of embodiment, be connected with planet carrier St-P2 not with gear ring Ho-P2 by the sun gear So-P2 of the 4th switching member K2 second planetary gear set P2.
Figure 10 schematically shows the speed changer G according to the present invention the 8th kind of embodiment.Different from first to the 6th kind of embodiment, be not sun gear So-P2 by the 4th switching member K2 but planet carrier St-P2 is connected with gear ring Ho-P2.
The first to eight kind of embodiment of speed changer has nine forward gears 1 to 9 and the R that reverses gear respectively, and the formation of gear 1-9, R for good grounds the first to eight kind of embodiment enforcement for be identical.
Figure 11 schematically shows the speed changer G according to the present invention the 9th kind of embodiment.In the 9th kind of embodiment, speed changer G has the 7th switching member K5.Can be connected with the 8th axle W8 by the 7th switching member K5 first axle W1.
Figure 12 illustrates the gearshift figure of the speed changer G according to the present invention the 9th kind of embodiment.At this to go explanation ten forward gears 21 to 210 and the 2R that reverses gear.In phase assortment, represent which switching member B1, B2, K1, K2, K3, K4, K5 must be closed, to realize corresponding gear 21-210,2R by X.First forward gear 21 is formed by closed first switching member B1, the second switching member B2, the 6th switching member K4 and the 7th switching member K5.The formation be formed in corresponding to first to the 9th forward gear 1-9 of first to the 8th kind of embodiment in the 9th kind of embodiment of the second to the tenth forward gear 22-210, opens in the second to the tenth forward gear 21-210 at this 7th switching member K5.The formation of the 2R that reverses gear of the 9th kind of embodiment is identical with the formation of reversing gear in first to the 8th kind of embodiment, and the 7th switching member K5 opens reversing gear in 2R.
Reference numerals list
G speed changer
GG case of transmission
GW1 transmission input shaft
GW2 transmission output shaft
B1 first switching member
B2 second switching member
K1 the 3rd switching member
K2 the 4th switching member
K3 the 5th switching member
K4 the 6th switching member
K5 the 7th switching member
P1 first planet gear train
P2 second planetary gear set
P3 third planet gear train
P4 fourth planet gear train
The sun gear of So-P1 first planet gear train
The planet carrier of St-P1 first planet gear train
The gear ring of Ho-P1 first planet gear train
The sun gear of So-P2 second planetary gear set
The planet carrier of St-P2 second planetary gear set
The gear ring of Ho-P2 second planetary gear set
The sun gear of So-P3 third planet gear train
The planet carrier of St-P3 third planet gear train
The gear ring of Ho-P3 third planet gear train
The sun gear of So-P4 fourth planet gear train
The planet carrier of St-P4 fourth planet gear train
The gear ring of Ho-P4 fourth planet gear train
W1 first axle
W2 second axle
W3 the 3rd axle
W4 the 4th axle
W5 the 5th axle
W6 the 6th axle
W7 the 7th axle
W8 the 8th axle
1-9 first is to the 9th forward gear
21-210 first is to the tenth forward gear
R/2R reverses gear
Claims (14)
1. a speed changer (G), comprise four planetary gear set (P1, P2, P3, P4), multiple axle (W1-W8) and first, second, 3rd, 4th and the 5th switching member (B1, B2, K1, K2, K3), the selectivity of these switching members engages the different drive ratios caused between transmission input shaft (GW1) and transmission output shaft (GW2), first axle (W1) is for good and all connected with the planet carrier (St-P3) of transmission input shaft (GW1) and third planet gear train (P3), second axle (W2) is for good and all connected with the planet carrier (St-P1) of transmission output shaft (GW2) and first planet gear train (P1), 3rd axle (W3) for good and all to connect with the sun gear (So-P3) of third planet gear train (P3) and can be fixed into and can not relatively rotate via the first switching member (B1), 5th axle (W5) is for good and all connected with the gear ring (Ho-P2) of the second planetary gear set (P2), 6th axle (W6) is for good and all connected with the gear ring (Ho-P1) of first planet gear train (P1), the gear ring (Ho-P3) of third planet gear train (P3) is for good and all connected with the sun gear (So-P2) of the second planetary gear set (P2) and forms the constituent element of the 7th axle (W7), 8th axle (W8) is for good and all connected with the planet carrier (St-P2) of the second planetary gear set (P2), first axle (W1) can be connected with the sun gear (So-P4) of fourth planet gear train (P4) via the 3rd switching member (K1), two elements of the second planetary gear set (P2) are connected to each other by the 4th switching member (K2), make the gear ring (Ho-P2) of second planetary gear set (P2) when the 4th switching member (K2) is closed, planet carrier (St-P2) and sun gear (So-P2) have same rotational speed, and the second axle (W2) can be connected with the 8th axle (W8) via the 5th switching member (K3), it is characterized in that, described speed changer (G) comprises the 6th switching member (K4), 5th axle (W5) can be connected with the sun gear of fourth planet gear train (P4) (So-P4) by the 6th switching member.
2. speed changer according to claim 1 (G), it is characterized in that, 4th axle (W4) is fixed into can not relatively rotates by the second switching member (B2), and the 3rd axle (W3) is for good and all connected with the sun gear (So-P1) of first planet gear train (P1), when fourth planet gear train (P4) is configured to negative ratio gear group, the gear ring (Ho-P4) of fourth planet gear train (P4) is the constituent element of the 4th axle (W4) and the 6th axle (W6) is for good and all connected with the planet carrier (St-P4) of fourth planet gear train (P4), and when fourth planet gear train (P4) is configured to positive drive than gear train, the planet carrier (St-P4) of fourth planet gear train (P4) is the constituent element of the 4th axle (W4) and the 6th axle (W6) is for good and all connected with the gear ring (Ho-P4) of fourth planet gear train (P4).
3. speed changer according to claim 1 (G), is characterized in that, the 3rd axle (W3) is for good and all connected with the sun gear (So-P1) of first planet gear train (P1), when fourth planet gear train (P4) is configured to negative ratio gear group, 6th axle (W6) can be connected with the planet carrier (St-P4) of fourth planet gear train (P4) via the second switching member (B2), the gear ring (Ho-P4) of fourth planet gear train (P4) is the constituent element of the 4th axle (W4) and is for good and all fixed into and can not relatively rotates, and when fourth planet gear train (P4) is configured to positive drive than gear train, 6th axle (W6) can be connected with the gear ring (Ho-P4) of fourth planet gear train (P4) via the second switching member (B2), the planet carrier (St-P4) of fourth planet gear train (P4) is the constituent element of the 4th axle (W4) and is for good and all fixed into and can not relatively rotates.
4. speed changer according to claim 1 (G), it is characterized in that, 3rd axle (W3) can be connected with the sun gear (So-P1) of first planet gear train (P1) via the second switching member (B2), and the 4th axle (W4) is fixed into and can not relatively rotates, when fourth planet gear train (P4) is configured to negative ratio gear group, the gear ring (Ho-P4) of fourth planet gear train (P4) is the constituent element of the 4th axle (W4) and the 6th axle (W6) is for good and all connected with the planet carrier (St-P4) of fourth planet gear train (P4), and when fourth planet gear train (P4) is configured to positive drive than gear train, the planet carrier (St-P4) of fourth planet gear train (P4) is the constituent element of the 4th axle (W4) and the 6th axle (W6) is for good and all connected with the gear ring (Ho-P4) of fourth planet gear train (P4).
5. the speed changer (G) according to any one of the claims, it is characterized in that, speed changer (G) has nine forward gears (1-9), first forward gear (1) is by closed first switching member (B1), second switching member (B2), 3rd switching member (K1) and the 6th switching member (K4) are formed, second forward gear (2) is by closed first switching member (B1), second switching member (B2), 4th switching member (K2) and the 6th switching member (K4) are formed, 3rd forward gear (3) is by closed second switching member (B2), 3rd switching member (K1), 4th switching member (K2) and the 6th switching member (K4) are formed, 4th forward gear (4) is by closed second switching member (B2), 4th switching member (K2), 5th switching member (K3) and the 6th switching member (K4) are formed, 5th forward gear (5) is by closed second switching member (B2), 3rd switching member (K1), 4th switching member (K2) and the 5th switching member (K3) are formed, 6th forward gear (6) is by closed second switching member (B2), 3rd switching member (K1), 5th switching member (K3) and the 6th switching member (K4) are formed, 7th forward gear (7) is by closed 3rd switching member (K1), 4th switching member (K2), 5th switching member (K3) and the 6th switching member (K4) are formed, 8th forward gear (8) is by closed first switching member (B1), 3rd switching member (K1), 5th switching member (K3) and the 6th switching member (K4) are formed, and the 9th forward gear (9) is by closed first switching member (B1), 4th switching member (K2), 5th switching member (K3) and the 6th switching member (K4) are formed.
6. the speed changer (G) according to any one of the claims, is characterized in that, the 8th axle (W8) is connected by the 7th switching member (K5) with the first axle (W1).
7. speed changer according to claim 6 (G), is characterized in that, the 7th switching member (K5) does not have infinitely variable torque transmission capacity, and is especially configured to castellated switching member or synchronizer.
8. according to claim 6 or speed changer according to claim 7 (G), it is characterized in that, described speed changer (G) has ten forward gears (21-210), wherein, first forward gear (21) is by closed first switching member (B1), second switching member (B2), 6th switching member (K4) and the 7th switching member (K5) are formed, second forward gear (22) is by closed first switching member (B1), second switching member (B2), 3rd switching member (K1) and the 6th switching member (K4) are formed, 3rd forward gear (23) is by closed first switching member (B1), second switching member (B2), 4th switching member (K2) and the 6th switching member (K4) are formed, 4th forward gear (24) is by closed second switching member (B2), 3rd switching member (K1), 4th switching member (K2) and the 6th switching member (K4) are formed, 5th forward gear (25) is by closed second switching member (B2), 4th switching member (K2), 5th switching member (K3) and the 6th switching member (K4) are formed, 6th forward gear (26) is by closed second switching member (B2), 3rd switching member (K1), 4th switching member (K2) and the 5th switching member (K3) are formed, 7th forward gear (27) is by closed second switching member (B2), 3rd switching member (K1), 5th switching member (K3) and the 6th switching member (K4) are formed, 8th forward gear (28) is by closed 3rd switching member (K1), 4th switching member (K2), 5th switching member (K3) and the 6th switching member (K4) are formed, 9th forward gear (29) is by closed first switching member (B1), 3rd switching member (K1), 5th switching member (K3) and the 6th switching member (K4) are formed, tenth forward gear (210) is by closed first switching member (B1), 4th switching member (K2), 5th switching member (K3) and the 6th switching member (K4) are formed.
9. the speed changer (G) according to any one of the claims, is characterized in that, fourth planet gear train (P4) is configured to positive drive and compares gear train.
10. the speed changer (G) according to any one of the claims, it is characterized in that, four switching members in each gear (1-9,21-210, R, 2R) of speed changer (G) in closed all six or seven switching members (B1, B2, K1, K2, K3, K4, K5).
11. speed changers (G) according to any one of the claims, it is characterized in that, the second switching member (B2) does not have infinitely variable torque transmission capacity and is especially configured to castellated switching member or synchronizer.
12. speed changers (G) according to any one of the claims, it is characterized in that, reverse gear (R, 2R) is formed by closed first switching member (B1), the second switching member (B2), the 5th switching member (K3) and the 6th switching member (K4).
13. speed changers (G) according to any one of the claims, it is characterized in that, third planet gear train (P3) is arranged on the radially inner side of the second planetary gear set (P2).
14. 1 kinds of power assembly systems for Motor Vehicle, comprise the speed changer (G) according to any one of claim 1 to 13.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014213695.4 | 2014-07-15 | ||
| DE102014213695.4A DE102014213695A1 (en) | 2014-07-15 | 2014-07-15 | transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105276143A true CN105276143A (en) | 2016-01-27 |
| CN105276143B CN105276143B (en) | 2019-02-19 |
Family
ID=55021623
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510410471.4A Expired - Fee Related CN105276143B (en) | 2014-07-15 | 2015-07-14 | Speed changer and power assembly system for motor vehicle |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US9746053B2 (en) |
| CN (1) | CN105276143B (en) |
| DE (1) | DE102014213695A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107989967A (en) * | 2016-10-26 | 2018-05-04 | 腓特烈斯港齿轮工厂股份公司 | Speed changer for motor vehicle |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6079584B2 (en) * | 2013-11-25 | 2017-02-15 | マツダ株式会社 | Automatic transmission |
| US9651118B2 (en) * | 2014-03-20 | 2017-05-16 | Gm Global Technology Operations, Llc | Multi-speed transmission |
| US10445506B2 (en) | 2016-03-30 | 2019-10-15 | Airwatch Llc | Detecting vulnerabilities in managed client devices |
| US11561860B2 (en) | 2017-11-13 | 2023-01-24 | Weka.IO Ltd. | Methods and systems for power failure resistance for a distributed storage system |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1573167A (en) * | 2003-05-27 | 2005-02-02 | 丰田自动车株式会社 | Multistage transmission |
| DE102005014592A1 (en) * | 2005-03-31 | 2006-10-19 | Zf Friedrichshafen Ag | Multi-speed transmission |
| CN103328856A (en) * | 2010-12-21 | 2013-09-25 | 腓特烈斯港齿轮工厂股份公司 | Multistep gear mechanism of planetary design |
| CN103573934A (en) * | 2012-08-08 | 2014-02-12 | 福特全球技术公司 | Multiple speed transmission |
| CN103827545A (en) * | 2011-09-27 | 2014-05-28 | Zf腓德烈斯哈芬股份公司 | Planetary transmission |
| CN103912641A (en) * | 2013-01-03 | 2014-07-09 | 福特全球技术公司 | Multi-speed transmission |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006016191B4 (en) * | 2006-04-06 | 2011-08-18 | ZF Friedrichshafen AG, 88046 | Multi-speed transmission |
| US8133148B2 (en) * | 2009-02-17 | 2012-03-13 | GM Global Technology Operations LLC | Multi-speed transmission having four planetary gear sets |
| US8152683B2 (en) * | 2009-06-26 | 2012-04-10 | GM Global Technology Operations LLC | Eight to thirteen speed automatic transmission |
| US8343005B2 (en) * | 2010-04-15 | 2013-01-01 | GM Global Technology Operations LLC | Multi-speed transmission having four planetary gear sets |
| US8353801B2 (en) * | 2011-01-10 | 2013-01-15 | GM Global Technology Operations LLC | Multi-speed transmission |
| US8715131B2 (en) * | 2011-11-30 | 2014-05-06 | Gm Global Technology Operations | Multi-speed transmission having a stacked planetary gear set |
| DE102012201684A1 (en) * | 2012-02-06 | 2013-08-08 | Zf Friedrichshafen Ag | Multi-speed transmission |
| US8926469B2 (en) * | 2012-08-22 | 2015-01-06 | Gm Global Technology Operations, Llc | Multi-speed transmission |
| JP5698288B2 (en) * | 2013-03-07 | 2015-04-08 | 本田技研工業株式会社 | Automatic transmission |
-
2014
- 2014-07-15 DE DE102014213695.4A patent/DE102014213695A1/en not_active Withdrawn
-
2015
- 2015-07-14 CN CN201510410471.4A patent/CN105276143B/en not_active Expired - Fee Related
- 2015-07-15 US US14/799,864 patent/US9746053B2/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1573167A (en) * | 2003-05-27 | 2005-02-02 | 丰田自动车株式会社 | Multistage transmission |
| DE102005014592A1 (en) * | 2005-03-31 | 2006-10-19 | Zf Friedrichshafen Ag | Multi-speed transmission |
| CN103328856A (en) * | 2010-12-21 | 2013-09-25 | 腓特烈斯港齿轮工厂股份公司 | Multistep gear mechanism of planetary design |
| CN103827545A (en) * | 2011-09-27 | 2014-05-28 | Zf腓德烈斯哈芬股份公司 | Planetary transmission |
| CN103573934A (en) * | 2012-08-08 | 2014-02-12 | 福特全球技术公司 | Multiple speed transmission |
| CN103912641A (en) * | 2013-01-03 | 2014-07-09 | 福特全球技术公司 | Multi-speed transmission |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107989967A (en) * | 2016-10-26 | 2018-05-04 | 腓特烈斯港齿轮工厂股份公司 | Speed changer for motor vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102014213695A1 (en) | 2016-01-21 |
| US9746053B2 (en) | 2017-08-29 |
| US20160017962A1 (en) | 2016-01-21 |
| CN105276143B (en) | 2019-02-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103270339B (en) | The multiple-speed gear-box of planetary gear construction mode | |
| CN107806497B (en) | Transmission for a motor vehicle and drive train for a motor vehicle | |
| US20140364271A1 (en) | Transmission for a motor vehicle | |
| JP6942739B2 (en) | Automotive transmissions and automotive drivetrains | |
| CN105276143A (en) | Transmission | |
| KR101714155B1 (en) | Transmission for vehicles | |
| CN105317946A (en) | Transmission | |
| CN104334921A (en) | Multi-speed gearbox | |
| CN108291615B (en) | Transmission for a motor vehicle and drive train for a motor vehicle having such a transmission | |
| KR101745104B1 (en) | Transmission for vehicles | |
| CN104334920A (en) | Multi-speed gearbox | |
| KR20180138222A (en) | Transmission for vehicles | |
| KR101724848B1 (en) | Transmission for vehicles | |
| KR20190009449A (en) | Transmission for vehicles | |
| CN104395641A (en) | Multi-speed gearbox | |
| CN108291614B (en) | Transmission for a motor vehicle and motor vehicle drive train having such a transmission | |
| US20190291564A1 (en) | Transmission for a Motor Vehicle, and Drive Train for a Motor Vehicle | |
| US20160017961A1 (en) | Transmission | |
| CN107339375A (en) | The speed changer of motor vehicle and the power assembly system with speed changer of motor vehicle | |
| KR101714154B1 (en) | Transmission for vehicles | |
| CN106555841B (en) | Transmission for a motor vehicle | |
| US20190085951A1 (en) | Multi-stage transmission for vehicles | |
| CN109906323A (en) | The speed changer of motor vehicle | |
| CN109139824A (en) | Transmission for a vehicle | |
| KR101724858B1 (en) | Transmission for vehicles |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20190219 Termination date: 20210714 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |